CN1815025A - Horizontal type orbiting vane compressor - Google Patents
Horizontal type orbiting vane compressorDownload PDFInfo
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- CN1815025A CN1815025ACNA2005100915656ACN200510091565ACN1815025ACN 1815025 ACN1815025 ACN 1815025ACN A2005100915656 ACNA2005100915656 ACN A2005100915656ACN 200510091565 ACN200510091565 ACN 200510091565ACN 1815025 ACN1815025 ACN 1815025A
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- pump
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- valve
- rotating shaft
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- 230000006835compressionEffects0.000claimsabstractdescription69
- 238000007906compressionMethods0.000claimsabstractdescription69
- 239000003507refrigerantSubstances0.000claimsabstractdescription24
- 238000005086pumpingMethods0.000claimsdescription12
- 230000030279gene silencingEffects0.000claimsdescription8
- 230000002093peripheral effectEffects0.000claimsdescription6
- 238000000926separation methodMethods0.000claimsdescription3
- 238000010586diagramMethods0.000description4
- 238000004378air conditioningMethods0.000description3
- 230000000694effectsEffects0.000description3
- 230000015572biosynthetic processEffects0.000description2
- 239000000446fuelSubstances0.000description2
- 238000001816coolingMethods0.000description1
- 238000000034methodMethods0.000description1
- 238000012986modificationMethods0.000description1
- 230000004048modificationEffects0.000description1
- 230000003442weekly effectEffects0.000description1
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Classifications
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Technical field
The present invention relates to a kind of rotating blade compressor, it can form compression chamber in the scroll inboard and the outside of orbiting vane along with the moving motion that scroll carries out in the running space defined in the cylinder, especially, the present invention relates to a kind of horizontal type orbiting vane compressor with horizontal structure.
Background technique
In general, rotating blade compressor (orbiting vane compressor) is configured to carry out moving by orbiting vane in having the cylinder of inlet and moves and compress the refrigerant gas of introducing in the cylinder.Various types of rotating blade compressors of classifying have been disclosed according to its profile.
Fig. 1 is the integrally-built longitdinal cross-section diagram that traditional rotary rotating blade compressor is shown.As shown in Figure 1, driver element D and the compression unit P that is arranged on driver element D below are installed in the housing 1, and driver element D and compression unit P are sealed simultaneously.Driver element D and compression unit P interconnect viavertical rotation axis 6, and thisrotating shaft 6 haseccentric part 6a.
Driver element D comprises:stator 2, and it is fixedly set in the housing 1; Androtor 3, it is arranged at and is used for rotating throughrotor 3 vertically extendingrotating shafts 6 in thestator 2 when givingrotor 3 supply of current.
Compression unit P comprises orbiting vane 4, and itseccentric part 6a by rotatingshaft 6 carries out the moving motion in cylinder 5.Along with orbiting vane 4 carries out the moving motion incylinder 5,51 refrigerant gas of introducing cylinder 5 are compressed by entering themouth.Ring 52 in cylinder 5 has.Between the inwall ofinterior ring 52 and cylinder 5, be limited with therunning space 53 of annular.Thescroll 40 of orbiting vane 4 carries out the moving motion in running space 53.As a result, formed compression chamber respectively in the inside and outside both sides ofscroll 40.
Be respectively arranged with main bearing 7 and auxilliary bearing 7a in the upper and lower of compression unit P, the opposite end of its supporting revolving shaft 6.Auxilliary bearing 7a hasdischarge side 8a, anddischarge side 8a is limited by silencing apparatus 8.Discharge side 8a is connected totubulose discharge route 9, andtubulose discharge route 9 vertical extent pass compression unit P andmain bearing 7, are drained into the housing 1 bydischarge route 9 from refrigerant compressed gas.
Also unaccounted reference character 11 is represented inlet duct, and 12 represent outer pipe, and 10a representative is used to prevent the Oudan ring (Oldham ' s ring) of scroll 40 rotations of orbiting vane 4.
When giving driver element D supply of current, thereforerotor 3 rotations of driver element D, are passedrotor 3 vertically extendingrotating shafts 6 and are also rotated.Along with the rotation of rotatingshaft 6, the orbiting vane 4 that is connected on theeccentric part 6a of rotatingshaft 6 carries out the moving motion.
As a result, thescroll 40 of orbiting vane 4 carries out the moving motion in the runningspace 53 of cylinder 5, introduces the refrigerant gas of cylinder 5 byinlet 51 with compression in the compression chamber in the inboard that is formed atscroll 40 respectively and the outside.Refrigerant compressed gas is discharged among thedischarge side 8a by the interior outer vent (not shown) that is formed at cylinder 5 and auxilliary bearing 7a.The higher pressure refrigerant gas of having discharged is introduced in the housing 1 by discharge route 9.At last, refrigerant compressed gas is discharged to outside the rotating blade compressor byouter pipe 12.
Fig. 2 is the top cross-sectional view that the traditional rotating blade compressor squeeze operation shown in Fig. 1 is shown.
As shown in Figure 2, thescroll 40 of the orbiting vane 4 of compression unit P carries out the moving motion in the runningspace 53 of cylinder 5, and as shown by arrows, it introduces the refrigerant gas of runningspace 53 byinlet 51 in order to compression.The moving motion of thescroll 40 of orbiting vane 4 will be described in detail below.
In the initial moving position of thescroll 40 of the orbiting vane 4 of compression unit P (promptly, 0 degree moving position) locates,refrigerant gas 51 is introduced into the interior suction chamber A1 that is arranged at scroll 40 inboards by entering the mouth, and, compress in being arranged at the external compression chamber B2 in scroll 40 outsides, external compression chamber B2 is not communicated withinlet 51 and outer vent 53b simultaneously.Refrigerant gas compresses in interior compression chamber A2, and refrigerant compressed gas has been discharged to outside the interior compression chamber A2 simultaneously.
In 90 degree moving positions of thescroll 40 of the orbiting vane 4 of compression unit P, also compress among the compression chamber B2 outside, and nearly all gas of refrigerant compressed be discharged to by inner outlet 53a in outside the compression chamber A2.In this stage, outer suction chamber B1 occurred, thereby refrigerantgas 51 is incorporated among the outer suction chamber B1 by entering the mouth.
In 180 degree moving positions of thescroll 40 of the orbiting vane 4 of compression unit P, interior suction chamber A1 disappears.Especially, interior suction chamber A1 has become interior compression chamber A2, therefore, compresses in interior compression chamber A2.In this stage, external compression chamber B2 is communicated with outer vent 53b.Subsequently, refrigerant compressed gas is discharged to outside the B2 of external compression chamber by outer vent 53b.
In 270 degree moving positions of thescroll 40 of the orbiting vane 4 of compression unit P, nearly all gas of refrigerant compressed is discharged to outside the B2 of external compression chamber by outer vent 53b, and also will compress in interior compression chamber A2.Equally also compress again among the suction chamber B1 outside.When the orbiting vane 4 further movings 90 of compression unit P were spent, outer suction chamber B1 disappeared.Especially, outer suction chamber B1 becomes and is external compression chamber B2, therefore, compresses continuously among the compression chamber B2 outside.As a result, thescroll 40 of the orbiting vane 4 of compression unit P turns back to the initial moving position of thescroll 40 of orbiting vane 4.By this way, the moving motion of 360 degree weekly of thescroll 40 of the orbiting vane 4 of compression unit P has just been finished.The moving motion of thescroll 40 of the orbiting vane 4 of compression unit P is carried out in a continuous manner.
Traditional rotary rotating blade compressor with said structure is vertically arranged rectilinear rotating blade compressor.When rectilinear rotating blade compressor is installed in the outdoor unit of air-conditioning, can increase the size of outdoor unit relatively, because rectilinear rotating blade compressor has occupied big relatively installing space in outdoor unit, so the miniaturization of outdoor unit is difficulty very.On the other hand, horizontal type orbiting vane compressor flatly is installed in below the cooling fan of outdoor unit of air-conditioning, and therefore, the miniaturization of outdoor unit is easy to realize.Thereby, increased demand to horizontal type orbiting vane compressor.Yet, when the design horizontal type orbiting vane compressor, must the oil supply structure of horizontal type orbiting vane compressor be thought better of.
Summary of the invention
Therefore, in view of the above problems, created the present invention, and the purpose of this invention is to provide a kind of horizontal type orbiting vane compressor, it can form compression chamber in the inboard and the outside of the scroll of orbiting vane along with the moving motion that scroll carries out in the running space defined in the cylinder.
Another object of the present invention provides a kind of horizontal type orbiting vane compressor that can eliminate the problem relevant with fuel feeding.
A further object of the present invention provides and a kind ofly can increase the horizontal type orbiting vane compressor of flow velocity of oil by improving oil supply structure.
According to the present invention, can realize above-mentioned and other purpose by a kind of horizontal type orbiting vane compressor is provided, this compressor comprises: horizontally disposed housing, it has inlet duct and outer pipe; Compression unit, it is arranged in this housing and is positioned at a side of horizontally disposed rotating shaft, thus this compression unit rotates by driver element, is used for compression refrigerant gas; And oil supply unit, its moving motion by the orbiting vane in this compression unit supplies to the oilhole that extends through this rotating shaft with oil from oil groove.
Preferably, this rotating shaft is set to the opposite end of this rotating shaft and is rotatably supported by main bearing and auxilliary bearing respectively, this main bearing is assisted the opposite side that bearing is arranged on this compression unit with being somebody's turn to do, and this horizontal type orbiting vane compressor also comprises: silencing apparatus, itself and the adjacent setting of outlet that should assist bearing; And discharge route, it is formed in this silencing apparatus, and this discharge route extends through this compression unit and is communicated with the discharge side that is limited by this silencing apparatus.
Preferably, this compression unit comprises: cylinder, and it has the running space that limits between the inwall of this cylinder and interior ring; And orbiting vane, it has the scroll that is used to carry out the moving motion in the running space that is arranged on this cylinder.
Preferably, compression chamber and external compression chamber in this running space is divided into by this scroll; And this cylinder has a pair of outlet, and this is communicated with compression chamber and this external compression chamber in this respectively outlet.
Preferably, this oil supply unit comprises: oil pump is used for oil is supplied to this rotating shaft from oil groove; And oil-in pipe and oil export pipe, it is separately positioned on the opposite side of this oil pump, and this oil-in pipe is installed in this oil groove, so that oilyly be introduced into this oil pump from this oil groove by this oil-in pipe, and this oil export pipe is communicated with this rotating shaft.
Preferably, this oil pump comprises: pumping parts (pumping part), and pumping operation is carried out in its moving motion by this orbiting vane, and these pumping parts have pump case; Pump intake and pump discharge, it is formed at the opposite side of the pump case of these pumping parts respectively, and this pump intake and this pump discharge are horizontally disposed with, and this pump intake is coaxial with this pump discharge simultaneously; And inlet side one-way valve and outlet side one-way valve, it is installed in respectively on this pump intake and this pump discharge.
Preferably, these pumping parts comprise: piston, and it is arranged in this pump case, and the elastic force that is used for the moving motion by this orbiting vane and is arranged on the spring of this pump case carries out the vertical linearity to-and-fro motion.
Preferably, this inlet side one-way valve comprises: pump intake and opposite side that valve casing, one side are connected to this pump case are connected to this oil-in pipe; And the valve break, it is fixedly set in the outlet side of this valve casing; And this outlet side one-way valve comprises: pump discharge and opposite side that valve casing, one side are connected to this pump case are connected to this oil export pipe; And the valve break, it is fixedly installed on the outlet side of this valve casing.
Preferably, this inlet side one-way valve also comprises: valve body, and it is arranged in this valve casing, thus the to-and-fro motion flatly of this valve body, this valve body has a plurality of oil grooves that form along this valve body outer peripheral portion; And this outlet side one-way valve also comprises: valve body, and it is arranged in this valve casing, thus the to-and-fro motion flatly of this valve body, this valve body has a plurality of oil grooves that form along the outer peripheral portion of this valve body.
Preferably, the diameter of the valve body of this inlet side one-way valve is greater than the diameter of this oil-in pipe and the diameter of this pump intake; And the diameter of the valve body of this outlet side one-way valve is greater than the diameter of this oil export pipe and the diameter of this pump discharge.
Preferably, this oil supply unit also comprises: propulsion device (propeller), the ingress that it is installed in the oilhole of this rotating shaft is used for increasing the flow velocity of oil that supplies to the oilhole of this rotating shaft by this oil export pipe.
Preferably, this oil supply unit also comprises: oil separation plate, it is arranged at the outlet side of the oilhole of this rotating shaft.
Description of drawings
From the detailed description below in conjunction with accompanying drawing, above and other objects of the present invention, feature and other advantage are understood easier quilt, wherein:
Fig. 1 is the integrally-built longitdinal cross-section diagram that traditional rotary rotating blade compressor is shown;
Fig. 2 is the top cross-sectional view that the squeeze operation of the traditional rotating blade compressor shown in Fig. 1 is shown;
Fig. 3 is the integrally-built longitdinal cross-section diagram that illustrates according to horizontal type orbiting vane compressor of the present invention;
Fig. 4 is the sectional view according to the oil pump of horizontal type orbiting vane compressor of the present invention shown in Fig. 3;
Fig. 5 is the stereogram that the valve body structure of the oil pump shown in Fig. 4 is shown;
Fig. 6 a illustrates the sectional view that oil pump moves under suction condition; And
Fig. 6 b illustrates the sectional view that oil pump moves under the discharge state.
Embodiment
Referring now to accompanying drawing the preferred embodiments of the present invention are described in detail.
Fig. 3 is the integrally-built longitdinal cross-section diagram that illustrates according to horizontal type orbiting vane compressor of the present invention.
As shown in Figure 3, horizontal type orbiting vane compressor comprises: seal casinghousing 100, and it flatly is provided with; Compression unit P, it is arranged at the side in the housing 100; And driver element D, it is arranged at the opposite side in the housing 100.Compression unit P and driver element D interconnect by the rotating shaft 150 with eccentric part 151.
Driver element D comprises: stator 110, and it is fixedly installed in the housing 100; And rotor 120, it is arranged in the stator 110, is used for rotating through when giving rotor 120 supply of current rotor 120 horizontally extending rotating shafts 150.
Compression unit P comprises: orbitingvane 130, it is used for carrying out the moving motion by the eccentric part 151 of rotating shaft 150 at cylinder 140.Along with the moving motion that orbitingvane 130 carries out in cylinder 140,141 refrigerant gas of introducing in the cylinder 140 are compressed by entering the mouth.Ring 142 in cylinder 140 has.Between interior ring 142 and cylinder 140 inwalls, be limited with round and round space 143.The scroll 130a of orbitingvane 130 carries out the moving motion in running space 143.As a result, form compression chamber respectively in the inboard and the outside of scroll 130a.
Opposite side at compression unit P is respectively arranged with main bearing 160 and auxilliary bearing 170, the opposite end of its supporting revolving shaft 150.Auxilliary bearing 170 has the discharge side 190 that is limited by silencing apparatus 180.Discharge side 190 is connected in the tubulose discharge route 200 that horizontal-extending passes compression unit P and main bearing 160, is discharged to the housing 100 by discharge route 200 from refrigerant compressed gas.
Below orbitingvane 130, be provided with oil supply unit.This oil supply unit comprises:oil pump 220 is used for oil is supplied to rotating shaft 150 from oil groove 103; And oil-inpipe 230 andoil export pipe 240, it is arranged at the opposite side of oil pump respectively.Oil-inpipe 230 is installed in the oil groove 103, be used for making oil to be introduced intooil pump 220 from oil groove 103 by oil-inpipe 230, andoil export pipe 240 is communicated with rotating shaft 150.
Also unaccounted reference character 101 is represented inlet duct, and 102 represent outer pipe, and 210 representatives are used to prevent the Oudan ring of the scroll 130a rotation of orbitingvane 130.
When giving driver element D supply of current, therefore rotor 120 rotations of driver element D, are passed rotor 120 horizontally extending rotating shafts 150 and are also rotated.Along with the rotation of rotating shaft 150, the orbitingvane 130 that is connected in the eccentric part 151 of rotating shaft 150 carries out the moving motion.
As a result, the scroll 130a of orbitingvane 130 in the running space 143 of cylinder 140, carry out moving motion with compression in the compression chamber in the inboard that is formed at scroll 130a respectively and the outside by 141 refrigerant gas that are incorporated into cylinder 140 that enter the mouth.Refrigerant compressed gas is discharged in the discharge side 190 by the interior outer vent (not shown) that is formed at cylinder 140 and auxilliary bearing 170.The higher pressure refrigerant gas of having discharged is introduced in the housing 100 by discharge route 200.Refrigerant compressed gas is discharged to outside the housing 100 by outer pipe 102 at last.
Along with the running of theoil pump 220 that is arranged at orbitingvane 130 belows, oil is introduced into theoil pump 220 from oil groove 103 by oil-inpipe 230, is fed into rotating shaft 150 byoil export pipe 240 then, and oilhole 152 longitudinal extensions pass rotating shaft 150.Preferably, propulsion device 250 is installed, is used for increasing the flow velocity of oil that supplies to the oilhole 152 of rotating shaft 150 byoil export pipe 240 in the ingress of the oilhole 152 of rotating shaft 150.Equally, the outlet side at the oilhole 152 of rotating shaft 150 is provided with oil separation plate (oilseparating plate) 260.
Fig. 4 is the sectional view thatoil pump 220 is shown.
As shown in Figure 4,oil pump 220 is a reciprocating pump, and it is configured to:piston 222 carries out the vertical linearity to-and-fro motion by the moving motion of orbitingvane 130 and the elastic force ofspring 223 in pump case 221.Pump case 221 is respectively arranged withpump intake 221a andpump discharge 221b at its oppositeside.Pump intake 221a andpump discharge 221b flatly are provided with, andpump intake 221a is coaxial withpump discharge 221b simultaneously.Onpump intake 221a andpump discharge 221b, be separately installed with inlet side one-way valve 224 and outlet side one-way valve 225.
Inlet side one-way valve 224 comprises:pump intake 221a and opposite side thatvalve casing 226, one side are connected topump case 221 are connected to oil-inpipe 230; Valvebreak 229, it is fixedly set in the outlet side ofvalve casing 226; Andvalve body 227, it is arranged in thevalve casing 226, thusvalve body 227 to-and-fro motion flatly.
The diameter ofvalve body 227 is greater than the diameter of oil-inpipe 230 and the diameter of pump intake 221a.As shown in Figure 5,valve body 227 forms the disc that has along a plurality of oil groove 227a of its outer peripheral portion formation.Oil-inpipe 230 andpump intake 221a are horizontally disposed with, and oil-inpipe 230 is coaxial withpump intake 221a simultaneously.
Outlet side one-way valve 225 comprises:pump discharge 221b and opposite side thatvalve casing 226, one side are connected topump case 221 are connected tooil export pipe 240; Valvebreak 229, it is fixedly installed on the outlet side ofvalve casing 226; Andvalve body 228, it is arranged in thevalve casing 226, thusvalve body 228 to-and-fro motion flatly.
The diameter ofvalve body 228 is greater than the diameter ofoil export pipe 240 and the diameter of pump discharge 221b.As shown in Figure 5,valve body 228 forms the disc that has along a plurality of oil groove 228a of its outer peripheral portion formation.Oil export pipe 240 andpump discharge 221b are horizontally disposed with, andoil export pipe 240 is coaxial withpump discharge 221b simultaneously.
Fig. 6 a and Fig. 6 b show the operation of oil pump 220.Fig. 6 a illustrates the sectional view thatoil pump 220 moves under suction condition, Fig. 6 b illustrates the sectional view thatoil pump 220 moves under the discharge state.
Be arranged on below the orbitingvane 130 and thepiston 222 that contact with orbitingvane 130, move downward, move up by thespring 223 that is arranged on the resiliency urgedpiston 222 that is used in thepump case 221 making progress then by the orbitingvane 130 that carries out the moving motion.In this way, by the moving motion of orbitingvane 130 and the elastic force ofspring 223,piston 222 carries out the vertical linearity to-and-fro motion inpump case 221, and has produced suction pressure and head pressure by the vertical linearity to-and-fro motion ofpiston 222 inpump case 221.
Whenpiston 222 moves up, shown in Fig. 6 a, inpump case 221, produced suction pressure, therefore, thevalve body 227 of inlet side one-way valve 224 and thevalve body 228 of outlet side one-way valve 225 move towards thepump intake 221a and thepump discharge 221b ofpump case 221 respectively.As a result, thevalve body 228 of outlet side one-way valve 225 closely contacts with thevalve casing 226 of outlet side one-way valve 225, and therefore, thepump discharge 221b ofpump case 221 is closed.Yet becausevalve break 229, thevalve body 227 of inlet side one-way valve 224 does not contact with thevalve casing 226 of inlet side one-way valve 224, and therefore, thepump intake 221a ofpump case 221 does not close.
So by oil-inpipe 230, inlet side one-way valve 224 andpump intake 221a, oil is introduced into (see figure 3) thepump case 221 from oil groove 103.
Whenpiston 222 moves down, shown in Fig. 6 b, inpump case 221, produced head pressure, therefore, thevalve body 227 of inlet side one-way valve 224 and thevalve body 228 of outlet side one-way valve 225 move towards oil-inpipe 230 andoil export pipe 240 respectively.As a result, thevalve body 227 of inlet side one-way valve 224 closely contacts with thevalve casing 226 of inlet side one-way valve 224, and therefore, oil-inpipe 230 is closed.Yet becausevalve break 229, thevalve body 228 of outlet side one-way valve 225 does not contact with thevalve casing 226 of outlet side one-way valve 225, and therefore,oil export pipe 240 is not closed.
So bypump discharge 221b, outlet side one-way valve 225 andoil export pipe 240, oil is fed into (see figure 3) the oilhole 152 of rotating shaft 150 frompump case 221.
From the above description can be clear, the invention provides a kind of horizontal type orbiting vane compressor, it can form compression chamber in the inboard and the outside of the scroll of orbiting vane along with the moving motion of scroll in the running space defined in the cylinder.So when horizontal type orbiting vane compressor was installed in the outdoor unit, the present invention had the effect that realizes the miniaturization of air-conditioning outdoor unit.
And by the pumping operation that the moving of orbiting vane is moved and realized, oil is supplied in the oilhole of rotating shaft forcibly.So the present invention has the effect that realizes steady and reliable fuel feeding.
In addition, propulsion device is installed in the ingress of rotating shaft oilhole.So the present invention has increase supplies to the flow velocity of the oil in the rotating shaft oilhole by the oil export pipe effect.
Although disclose the preferred embodiments of the present invention for illustrative purposes, it will be understood by those of skill in the art that do not breaking away from the disclosed scope and spirit of the present invention of appended claims, can carry out various modifications, additional and alternative.
Claims (12)
1. horizontal type orbiting vane compressor comprises:
Housing, it is horizontally disposed with and has inlet duct and an outer pipe;
Compression unit, it is arranged in this housing and is positioned at a side of horizontally disposed rotating shaft, thus this compression unit rotates by driver element, is used for compression refrigerant gas; And
Oil supply unit, its moving motion by the orbiting vane in this compression unit supplies to the oilhole that extends through this rotating shaft with oil from oil groove.
2. compressor as claimed in claim 1, wherein, this rotating shaft is set to the opposite end of this rotating shaft and is rotatably supported by main bearing and auxilliary bearing, and this main bearing is assisted the opposite side that bearing is separately positioned on this compression unit with being somebody's turn to do, and this compressor also comprises:
Silencing apparatus, itself and the adjacent setting of outlet that should assist bearing; And
Discharge route, it is formed in this silencing apparatus, and this discharge route extends through this compression unit and is communicated with discharge side that this silencing apparatus is limited.
3. compressor as claimed in claim 1, wherein, this compression unit comprises:
Cylinder, it has the running space that limits between the inwall of this cylinder and interior ring, and
Orbiting vane, it has the scroll that is used to carry out the moving motion in the running space that is arranged on this cylinder.
4. compressor as claimed in claim 3, wherein,
Compression chamber and external compression chamber in this running space is divided into by this scroll; And
This cylinder has a pair of outlet, and this is communicated with compression chamber and this external compression chamber in this respectively outlet.
5. compressor as claimed in claim 1, wherein, this oil supply unit comprises:
Oil pump, it is used for oil is supplied to this rotating shaft from oil groove; And
Oil-in pipe and oil export pipe, it is separately positioned on the opposite side of this oil pump,
This oil-in pipe is installed in this oil groove, so that oil is introduced into this oil pump from this oil groove by this oil-in pipe, and this oil export pipe is communicated with this rotating shaft.
6. compressor as claimed in claim 5, wherein this oil pump comprises:
The pumping parts, pumping operation is carried out in its moving motion by this orbiting vane, and these pumping parts have pump case;
Pump intake and pump discharge, it is formed at the opposite side of the pump case of these pumping parts respectively, and this pump intake and this pump discharge are horizontally disposed with, and this pump intake is coaxial with this pump discharge simultaneously; And
Inlet side one-way valve and outlet side one-way valve, it is installed in respectively on this pump intake and this pump discharge.
7. compressor as claimed in claim 6, wherein these pumping parts comprise:
Piston, it is arranged in this pump case, and the elastic force that is used for the moving motion by this orbiting vane and is arranged on the spring of this pump case carries out the vertical linearity to-and-fro motion.
8. compressor as claimed in claim 6, wherein this inlet side one-way valve comprises:
Pump intake and opposite side that valve casing, one side are connected to this pump case are connected to this oil-in pipe; And
The valve break, it is fixedly installed on the outlet side in this valve casing; And
This outlet side one-way valve comprises:
Pump discharge and opposite side that valve casing, one side are connected to this pump case are connected to this oil export pipe; And
The valve break, it is fixedly installed on the outlet side in this valve casing.
9. compressor as claimed in claim 8, wherein, this inlet side one-way valve also comprises:
Valve body, it is arranged in this valve casing, thus the to-and-fro motion flatly of this valve body, this valve body has a plurality of oil grooves that form along this valve body outer peripheral portion; And
This outlet side one-way valve also comprises:
Valve body, it is arranged in this valve casing, thus the to-and-fro motion flatly of this valve body, this valve body has a plurality of oil grooves that form along this valve body outer peripheral portion;
10. compressor as claimed in claim 9, wherein,
The diameter of the valve body of this inlet side one-way valve is greater than the diameter of this oil-in pipe and the diameter of this pump intake; And
The diameter of the valve body of this outlet side one-way valve is greater than the diameter of this oil export pipe and the diameter of this pump discharge.
11. compressor as claimed in claim 1, wherein, this oil supply unit also comprises:
Propulsion device, the ingress that it is installed in the oilhole of this rotating shaft is used for increasing the flow velocity of oil that supplies to the oilhole of this rotating shaft by this oil export pipe.
12. compressor as claimed in claim 1, wherein this oil supply unit also comprises:
Oil separation plate, it is arranged at the outlet side of the oilhole of this rotating shaft.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020050010703AKR100669890B1 (en) | 2005-02-04 | 2005-02-04 | Horizontal Slewing Vane Compressor |
| KR1020050010703 | 2005-02-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1815025Atrue CN1815025A (en) | 2006-08-09 |
| CN100467872C CN100467872C (en) | 2009-03-11 |
Family
ID=36780140
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100915656AExpired - Fee RelatedCN100467872C (en) | 2005-02-04 | 2005-08-23 | Horizontal type orbiting vane compressor |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20060177339A1 (en) |
| KR (1) | KR100669890B1 (en) |
| CN (1) | CN100467872C (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101973623B1 (en)* | 2012-12-28 | 2019-04-29 | 엘지전자 주식회사 | Compressor |
| KR101983049B1 (en)* | 2012-12-28 | 2019-09-03 | 엘지전자 주식회사 | Compressor |
| KR102197862B1 (en)* | 2016-08-30 | 2021-01-04 | 엘지전자 주식회사 | Compressor and clothes treatment apparatus having the same |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0367092A (en)* | 1989-08-07 | 1991-03-22 | Mitsubishi Electric Corp | Horizontal rotary compressor |
| KR940012888A (en)* | 1992-11-03 | 1994-06-24 | 백중영 | Random Code Processing Apparatus and Method of Wireless Transceiver |
| KR950010176B1 (en)* | 1992-12-31 | 1995-09-11 | 엘지전자주식회사 | Rotary compressor |
| KR960001190Y1 (en)* | 1993-07-22 | 1996-02-08 | 엘지전자주식회사 | Rotary compressor |
| JPH07247980A (en) | 1994-03-11 | 1995-09-26 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH07293470A (en) | 1994-04-26 | 1995-11-07 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH0921393A (en) | 1995-07-07 | 1997-01-21 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH0988858A (en) | 1995-09-29 | 1997-03-31 | Matsushita Refrig Co Ltd | Rotary compressor |
| KR100436864B1 (en)* | 2002-07-15 | 2004-06-22 | 황동일 | Vane compressor |
- 2005
- 2005-02-04KRKR1020050010703Apatent/KR100669890B1/ennot_activeExpired - Fee Related
- 2005-08-23CNCNB2005100915656Apatent/CN100467872C/ennot_activeExpired - Fee Related
- 2005-08-23USUS11/208,722patent/US20060177339A1/ennot_activeAbandoned
Also Published As
| Publication number | Publication date |
|---|---|
| CN100467872C (en) | 2009-03-11 |
| US20060177339A1 (en) | 2006-08-10 |
| KR100669890B1 (en) | 2007-01-19 |
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